Calculating machine



June 19, 1945. H. M. DUSTIN CALCULATING MACHINE Filed May 13, 1941 5 Sheets-Sheet' l it? etitiii:

INVENTOR Howard/14.003200 ATTORNEY S June 19, 1945. H. M/DUSTIN 2,378,472

CALCULATING MACHINE Filed May 15, 1941 5 Sheets-Sheet 2 ATTORNEYS June 19, 1945; H. M. DUSTIN CALCULATING MACHINE Filed May 13, 1941 5 SheetS -Sheet 3 ATTORNEYS June 19, 1945. H. M. DUSTIN CALCULATING MACHINE Filed May 13, 1941 5 Sheets-Sheet 4 VIIIIIIIIJH 2. ii... I

ATTORNEYS -lEl IEIE

June 19, 1945.

Filed May 15, 1941 INVENTOR j HowardMflusfm ATTORNEYS Patented June 19, 1945 2,378,472 CALCULATING MAoinNE Howard M. Dustin, Berkeley, Calif., assignor to Marchant Calculating Machine Company, a corporation of California Application May 13, 1941, Serial No. 393,207

6 Claims.

This invention relates to a calculating machine of the type designed to perform four cardinal calculations.

The invention more particularly refers to that type of calculating machine in which wselective transmission is incorporated between the operating member or hand-crank and the differential actuator, whereby a single operation of the operating member may be caused to insert an entry any selected number of times in the accumulator register. In such a calculating machine it is desirable to disengage the accumulator register from the actuator of the machine at the conclusion of each cycle of operation of the operating member and to engage the accumulator register and actuator and maintain such engagement throughout a suitable actuating period.

It is a general object of the present invention to provide an improved and simplified mechanism for effecting engagement and disengage ment between the accumulator register and the actuator.

It is a further object of the present invention to provide a mechanism capable of maintaining the accumulator register in engagement with the actuator during a plurality of-cycles of operations, which mechanism is operable independently of the numbers of cycles through which a machine is operated,

' It is a further object of the present invention to provide an improved and simplified mechanism for maintaining a desired setting of the selection mechanism during a plural cycle operation.

It'is a further object of the present invention to set and to maintain in the set position. certain members associated with a crawl carry type of accumulator mechanism.

Various other objects and advantages of the present invention will appear from the following description of a preferred form of machine embodying the present invention, for which purpose reference is made to the accompanying drawings, in which,

Figure 1 isa longitudinal section, as viewed from the right, showing the general arrangements of the parts of the machine.

Figure 2 is a detailed section, as viewed from the right, showing the members which constitute the centralizing and interlocking means for the selective speed transmission unit.

Figure 3 is a right side view of the mechanism for locking the selection levers in position while actuation is taking place.

Figures 4 to 7, inclusive, are detail views 0 parts of the selection mechanism.

Figure 8 is an enlarged view partly in section of two orders of the accumulator, showing the construction thereof.

Figure 9 is a right side view of the carriage showing parts of the accumulator planetary gear train.

Figure 10 is a developed plan view partly schematic and partly in section of the selective speed transmission unit, and its drive-to the actuator and related mechanisms.

Figure 11 is a right side view of the mechanism for releasing and for locking the actuator drive gears.

Figure 12 is a right side view of the actuator centralizer and the means for locking the actuator in full cycle position.

The machine embodying the invention includes a shiftable numeral wheel carriage having an accumulator register which is engaged with the actuator mechanism during the actuating period and disengaged therefrom subsequent to the actuating period to permit shifting of the carriage. The accumulator register is of the crawl carry type in which partial digital increments are transferred from adjacent numeral wheels in the process of carrying the tens. At the conclusion of an operation, therefore, the numeral wheels are backed up the amount of this partial increment so that they are brought into correct alignment.

In hand-operated calculating machines having mechanisms for conditioning the machine for calculation operation, such as shown in the Chase Patent No. 2,233,912, an enabling device is provided to control the conditioning mechanism in such a way that the latter is rendered effective at the beginning of the operation of the hand-crank. The enabling device is driven in time with the actuator and is adjusted during the initial operation thereof in such a way as to maintain the conditioning mechanism effective throughout a multicyclic operation of the actuator. At the conclusion of such a'multi-cyclic operation the hand crank is overdriven beyond its full cycle position and subsequently returned to its full cycle position, at which time the enabling device is readjusted to its initial position to permit return of the conditioning mechanism to disabled position so that shifting or clearing operations may subsequently be initiated. In the present machine, on the other hand, the enabling device is driven in time with the hand-crank independently of the cycles of the actuator, and enables and mainextra cyclic movement of the hand-crank.

Selecting and actuating mechanism The numeral keys I (Fig. 1), by means of which the factors are entered into the machine, are arranged in parallel rows of ten keys each, one such row being shown in the drawings. Each key I5 is mounted on a key stem I6 which is vertically slidable in a key frame 9 and normally maintained in raised position by a spring 6 compressed between a lug on the key stem and the key frame.

The keys are adapted to be latched down by a lock bar- (Fig. 1) having a hook 92 for each key, which snaps over the top of a part of the key stem when the key is depressed as described more fully in the Avery application, Serial No. 367,025, filed November 25, 1940.

A second bar has a series of notches 59 placed at intervals slightly less than the distance between the keys so that depression of the keys slides the bar towards the right different amounts. A lever 58 having a gear Segment 51 meshing with a pinion 56 integral with the numeral wheel 52 is pivotally mounted on a shaft 61. This lever is connected to the bar 50 so that the differential movement thereof in response to the depression of a selected key rotates the nu meral wheel 52 to the position indicative of the key depressed.

Also, underlying the numeral keys are a series of selection bars 45!) (Figs; 1 and 3), 440, 438, 420, and 4H] shown partly in Figs, 4 to 7, inclusive. The bar 450 (Fig. 1) is known as the 5 6 selection bar and is controlled by the five and six numeral keys to set the numeral wheel actuator, explained hereinafter, fora five or six actuation. This bar has a series of notches, notch 452 of which normally lies to the left of the five key stem so that depression of this key slides the bar towards the right from the neutral position shown. Similarly, a second notch 45f lies to the right of the six key stem and depression thereof moves the selection bar toward the left. The remaining notches 455 lie direct ly under the remaining keys so that depression thereof has no effect upon the bar. The other selection bars are related similarly to the other keys and effect a setting of the actuator in accordance with the keys depressed. These bars bring certain gears, explained hereinafter, into mesh and establish diffel'ential driving ratios between three actuator shafts I66, I61, and I68 (Fig. 1) and the product numeral wheels so that one cycle of the actuator shafts may drive the numeral wheels through 1 to 9 digital increments.

The actuator shafts I66, I61, I68 (Figs. 3 to '1 and 10), hereinafter referred to as the half,

quarter, and twelfth speed shafts, respectively, are common to all denominational orders of the machine and are connected to the driving mechanism through suitable gearing and transmission devices, shown in Fig. 10, so that shaft I66 rotates through 180, shaft I81 through 90, and shaft I68 rotates through 30 for each cycle of operation of the machine.

A gear I89 and an integral sleeve I19 (Figs. 1 and '7) are mounted on a shaft I10 in each denominational order and are adapted to be connected to the actuator gear train and driven by one of the three shafts I66, I61, or I68 at any one of nine different rates with respect to the driving means, said rates corresponding to the values delineated 0n the keys I5. Since this mechanism is repeated in each denominational order of the machine only one such order will be described in detail,

Five and sia: selection adjustment I61. Thus, if plate 412 is swung to the right, up-- on depression of the 5 key (Fig. 1) gear 413- (Fig. 3) will be brought into mesh with gear 416, whereupon the rotation of shaft I61 during each cycle of operation of the machine will ad vance the gear 41I five teeth; while if plate 412 is swung to the left, upon depression of the 6 key gear 418 will be carried into mesh with gear 415 and the rotation of shaft I 66 will advance the gear 4" six teeth during each cycle of operation of the machine. By this means, either a five or a six selection may be effected.

Four and seven selection adjustment Also, keyed-to the sleeve I19 is gear 411 (Fig. 4) and mounted for oscillation on a spacer carried by said sleeve adjacent this gear is a selection plate 418, on which are mounted idler gears 419 and 489 which are entrained with gear 411. Keyed to shaft I68 in alignment with idler 419 is a fourteen-tooth gear 48I, and keyed to shaft I61 in alignment with idler 419 is a sixteen-tooth gear 482. Thus, when the selection plate 418 is swung to the right (as viewed in Fig. 4) its idler 419 will mesh with the gear 482 and the 90 rotation of shaft I81 in each cycle will serveto advance the gear 411 four teeth; while, when the said plate 418 is swung toward the left, idler 419 will mesh with gear 48I and the 180 rotation of shaft I86 in each cycle will serve to advance the gear 411 seven teeth. By this means, either a seven or a four selection may be effected.

Three and eight selection adjustment Also, keyed upon sleeve I19 (Fig. 5) is a gear 483, and mounted to oscillate freely upon a spacer carried by the sleeve I19 adjacent this gear is a selection plate 484, similar to those above described and carrying idlers 485 and 486. Keyed to shaft I66 in alignment with idler 485 is a sixteen-tooth gear 481, and keyed to shaft I61 in alignment with idler 485 is a twelve-tooth gear 488. Thus, when plate 484 is swung to the left (as viewed in Fig. 5) its idler 485 will mesh with gear 481 and the 180 rotation of shaft I66 in each cycle will serve to advance the gear 483 eight teeth; while when plate 484 is swung toward the right, idler 488 will mesh with gear 488 and the 90 rotation of shaft I61 in each cycle of operation will serve to advance the gear 483 three teeth. By this means, either an eight or a three selection may be effected.

Two and nine selection adjustment Also, keyed to the sleeve I19 is a broad faced gear I 89 (Fig. 6), and freely mounted for oscillation on a spacer carried by the sleeve I19 on one side of this gear is a selection plate 480,

similar to those above described, and mounting idlers 290 and 29I. Keyed to shaft I66 in alignment with idler 29I is an eighteen-tooth gear 493, and keyed to shaft I68 is a twenty-four tooth gear 495 which meshes with a gear 494 rotatably mounted upon shaft I61 in alignment with idler 29L Thus, if plate 490 is swung to the left (as viewed in Fig. 6) idler 29I' will mesh with gear 493 and the 180 rotation of the shaft I66 in each cycle will serve to advance the gear I89 nine teeth; while, if the plate 490 is swung toward the right, the idler 29I will mesh with the gear 494 and the 30 rotation of shaft I68 in each cycle will drive gear 494 through gear 486 to advance the gear I89 two teeth. By this means, either a nine or a two selection may be effected.

One selection adjustment Mounted for oscillation on sleeve I19 at the opposite side of gear I89 is another selection plate 496 (Fig. 7) having mounted thereon intermeshing idler gears 491 and 498. Gear 498 is constantly enmeshed with gear I89, while gear 491 may mesh with the twenty-four tooth idler gear 499, which is rotatably mounted on shaft I61 when the plate 496 is swung to the right (as viewed in Fig. 7). This gear 499 is driven by a twelve-tooth gear 200 keyed on shaft I68 so that gear I89 will be advanced a single tooth upon a 30 rotation of gear 200 when plate 496 is swung to the right.

Zero selection adjustment A zero selection is effected by holding gear I89 against rotation. For this purpose, a pawl I (Fig. '1) is mounted upona shaft 202, so that when the plate 496 is swung to the left the edge of said plate will engage an ear 203 on pawl 20I and retain said pawl in engagement with the gear I89 after the shaft 202 is rocked, as hereinafter described.

The shaft 202 extends across all orders of the machine and one pawl 20I is provided for each decimal order. At the commencement of operation, shaft 202 is rocked counter-clockwise to a limited extent by a mechanism to be presently described, and when the machine comes to rest the shaft is returned in a clockwise direction. It will be noted that pawl 20I is provided with narrow keys 204 lying in wider key-ways in the shaft 202 and, therefore, when some value other than zero is selected in a given order the initial counter-clockwise rocking of shaft 202 will free pawl 20I so that upon rotation of sleeve I19 the gear I89 may rock its associated pawl 20I out of the way. However, if a zero is selected in a particular order, the associated plate engaging the lug 203 of the pawl 20I, as previously explained, will retain the pawl in engagement with the gear I89, notwithstanding the counter-clockwise movement of the shaft 202, because the key-way in which the keys 204 are engaged is wide enough to permit such limited rocking movement of the shaft 202 as is necessary in this operation. By this arrangement, when the selection plate 496 is swung toward the left, as viewed in Figure 8, the gear I89 is locked and the zero selection is effected.

It will be apparent from the foregoing that one of the five selection plates in each order is positioned during a selection operation to select either a numeral value or zero while the remaining four plates of that order are held in idle Selection locking provision Means are provided to lock the plurality of selection plates 412, 418, 484, 490, and 496 (Figs. 3, 4, 5, 6, and 7) in one of their three positions during the actuation period. A shaft II5 (Fig.

8) is rocked counter-clockwise just before the I actuation period by mechanisms explained hereinafter. A lever I83 is secured'to this shaft and is connected to a lever I84 pivoted on a shaft I08. A selection locking bail I85 is secured to lever I84 and extends across the machine so that a flange I86'thereon may be moved upwardly into one of the three notches I81 to lock all the selec tion plates in one of the three positions described hereinbefore. After the actuation cycles are completed, the shaft H5 is rocked back to the position shown, which rocking moves the flange I86 out of the notches I81 so that the plates may be moved to a new setting indicative of the next selection entered on the keys I5 (Fig. 1.)

Driving mechanism The operating cycle of the present machine is divided into three phases; a setting phase, an actuating phase, and a restore and shift phase of approximately twelve and one-half per cent, seventy-five per cent, and twelve and one-half per cent of the cycle, respectively.

Means are provided to enmesh the carriage drive gear 21I (Fig. 1) with the actuator pivot gear I89 during the setting phase, and to accomplish this a direct drive is established from the crank handle I00 (Figs. 1 and 10) to a dipping cam I08. Crank I00 is made integral with gear I03 and shaft I02. Gears I03, I04, I05, and I06 are constantly in mesh, and since gears I03 and I06 have the same number of teeth one turn of the crank I00 effects one complete rotation of gear I06 and of shaft I01 and cam I08 integral therewith.

On a stud I09 (Fig. l) is freely pivoted a bell crank IIO provided with a roller II I which lies in the plane of cam I08. A second roller I I3 is provided on said bell crank which cooperates with a downwardly extending arm I I4 to effect a rocking of shaft I I5 to which arm I I4 is secured. Also, integrally secured to shaft I I5 are two dipping arms I I6, on each of which are mounted two rollers I I? adapted to embrace the dipping bail 269. As described in the Avery Patent No. 2,271,240, this bail 269 is disposed laterally in the machine and is secured to the rear end of each of the carriage brace plates 266, so that when the bail'269 is lowered all gears 21I move into mesh with the actuator pivot gears I89. The cam I08 is so designed that it completes its rise in the first 45 of its rotation in either direction from the position shown in Figure 1, so that the carriage will be dipped and ready for actuation when the hand-crank cycle is twelve and one-half per cent complete.

Accumulator,

The actuation of the numeral wheels 219 is effected by mechanism, including the above-mentioned pivot gears I89 (Fig. 1) which mesh with the gears 2H mounted in the shiftable carriage. Gears 213 meshing with the gears 2' are integral with two plates 292 and 296 (Fig. 8) between which are .lournaled the planetary gears 293. These planetary gears revolve about a sun gear 299 and drive the ring gear 216 and its integral numeral wheel 219 in a manner more completely described in the Avery Patent No. 2,222,164, dated November 19, 1940, to which reference may be had for a full description of portions of the accumulator mechanism not specifically disclosed herein.

In addition to this direct actuation of the numeral wheels by the actuator unit, a tens carry mechanism is provided whereby one complete revolution of a numeral wheel will effect one-tenth of a revolution of the numeral wheel immediately to the left. This is accomplished through a direct ten to one planetary gear train from one numeral wheel to the next, which train consists of gear 280 (Fig. 8) integral with the numeral wheel 219, planetary gears 309 'and 300, ring gear 30I integral with the sun gear 299, and planetary gears 298 which drive the ring gear 216 integral with the next higher numeral wheel.

Numeral wheel aligning mechanism Obviously, if the numeral wheel to the right in Figure 8, for example, is driven one-half a revolut on or five digital increments, the numeral wheel to the left will be driven one-half of one-tenth of a revolution or half the distance between numerals. After the actuation is completed, it is necessary to back up the left-hand numeral wheel by the amount of this partial increment so that the numeral can be read through the dial opening in the carriage cover. For this purpose, a numeral wheel aligning cam 28I (Figs. 1 and 8) is made integral with the numeral wheel andis so shaped as to permit the cam follower 3I5 to be rocked upwardly from the position shown in Figure 1, by an amount proportional to the digit displayed on the numeral wheel. An ear 3 (Figs. 1 and 9) of a rocking segment 3I3 underlies the cam follower 3 I so as to limit the clockwise movement of said rocking segment in accordance with the current position of the cam follower 3 I5, thereby rocking the segment plate 304 which carries planetary gears 309 and 309. Therefore, these planetary gears are backed up by movement of the segment 304 through an angle which cancels the amount they are rotated by the gear 280, and, as explained more in detail in the last-mentioned Avery patent, the next higher dial is likewise backed up by the same partial increment it receives through the tens carry train.

In the present machine the numeral wheel aligning mechanism is disabled during positive operation in order to avoid the great resistance to numeral wheel rotation that would result if the cam followers 3I5 (Fig. 1) were to be simultaneously driven up the steep cam rises in a number of adjoining orders, as for example when a series of numeral wheels stand at nine and the lowest order of the series is driven by the actuator from nine to zero. -When operating negatively in division, however, it is necessary that the operator be immediately warned when an overdraft occurs and the numeral wheel aligning mechanism is not disabled during negative operation in a manner that will appear from the following description.

When the machine is operated negatively until the numeral wheels 219 are reduced to the zero position, shown in Figure 1, the cam followers 3I5 are rocked the farthest distance from the center of cams 28I. If a digit is again subtracted, the numeral wheel and its integral cam 28I are rotated clockwise, which allows the roller 3I6 to move from the extreme high or zero point of the cam to the extreme low or nine position. An ear 3 is formed on the segment 3I3 (Fig. 9) and underlies the cam follower 3I5 (Fig. 1) so that when said cam follower is released by cam 28I the spring 3l1 rocks the segment 3|; and cam follower 3I5 clockwise, and coincidentally rocks a second segment 304 (Fig. 9) counterclockwise. On the segment 304 are mounted two integral planetary gears 309 and 300 (Figs. 8 and 9), and during this counter-clockwise rocking of segment 304 the gear 309 revolves about the sun gear 280 and the second planetary gear 309 revolves inside the ring gear 30I, thus imparting counter-clockwise rotation to spider 300 and its integral sun gear 299.

The planetary gears 298 mesh with both sun gear 299 and ring gear 216, which latter is integral with spider 2H and the numeral wheels 21!. Therefore, the counter-clockwise rotation of sun gear 299 imparts clockwise rotation to sun gears 298 about their own centers and clockwise rotation to the next higher order numeral wheel 219 from zero to nine. Secured to this next higher order numeral wheel is also a cam 28l which is rotated to effect a repetition of the movements just described, from that order to the immediate higher order, thus setting up a carry wave to all nines leftward across the carriage.

From the above explanation, it will be noted that if the numeral wheel aligning mechanism were disabled until the completion of the current actuation the "carry wave" would likewise be delayed until the completion of that actuation,

and since the movement of the highest order accumulator numeral wheel from zero to nine serves to indicate an overdraft, this operation too would be delayed until the completion of actuation.

Mechanism has, therefore, been provided to free cam followers 3 I 5 from their cooperation with cams 28I during positive operation only, as described hereinafter.

A cam 60 (Figs. 1 and 10) is made integral with a gear 62, the unit thus formed being freely rotatable on shaft I56 and driven by a gear II8 keyed to shaft I01 (Fig. 10). The arrangement is such that cam 50 is rotated through the same angles and in the same direction as crank I00. As can be seen in Figure 1, a clockwise rotation of crank I00 and gear I 03 will rotate gear I04 counterclockwise, gear I05 clockwise, gears I08 and III (Fig. 10) counter-clockwise, and gear 82 and cam 60 clockwise (Fig. 1).

A stud 05 (Fig. 1) is secured to a frame of the machine and on it are mounted two levers 0i and 10, lever 66 having a downwardly extending arm 69 whichfollows the cam 50 and is normally held in the position shown in Fig. 1 by the spring 08. On the lever I0 is formed an ear II, which is adjacent the arm 69, and a second car H which is formed laterally toward the left side of, the machine and designed to operate in the plane of a lever I5. A spring I8 urges lever 10 in a clockwise direction to the limit provided by a stationary ear 8. A shaft is disposed laterally in the carriage of the machine and is supported by the lower carriage brace plates 206. One 01' the levers I5 is keyed to said shaft in each denominational order, so that no matter what position the carriage may be in the, ear 14 will contact one oi the levers I5 whenever it is rocked in a counter-clockwise direction. This counter-clockwise rocking of ear I4 will cause a clockwise rocking of shaft 80, and the members 16 which are provided in each order of the register will be rocked around and by contacting ear 3I8 will move cam followers 3I5 away from the cams 20L As stated above, cam 60 rotates in the same direction and at the same speed as the hand-crank I00. Therefore, when the hand-crank is rotated clockwise for positive actuation cam 60 will move tip '69 to the right (Fig. 1) and lever 68 in a counter-clockwise direction. Ear 1| on lever I will be effective to transmit this movement to ear 14, which movement is effective as previously described to rock the followers 3I5 away from the numeral wheel cams 28I. On the other hand, if the hand-crank is rotated counter-clockwise for negative operation, cam 60 will move tip 69 to'the left, which is away from the ear II, and, therefore, car 14 will not be moved and the followers 3I5 will remain in cooperation with the cams 28I.

Selective ration transmission The drive from the hand-crank to the actuator runs through a selective ratio transmission .unit,

, which consists of a series of gears I2I to I29, in-

and gear I04 is secured to shaft I20 so that this shaft will always rotate an angular amount equal to that of the crank.

Each of the gears I2I and I29 has welded thereto or otherwise made integral therewith a centralizer and interlocking disc I4I (Figs. 10 and 2). Keyways 142 are provided in the gears I2I to I29 and the discs I4I. These keyways are somewhat wider than the thickness of a key I40 to facilitate shifting of the key from one gear to another. As shown in Figure 10, the shaft I20 has a deep keyway cut in one side to receive the slidable key I40. It will be noted that the key terminates at its rightward end in a driving tongue, the length of which is slightly shorter than the combined thicknesses of a gear I2I to I29 and its respective disc I4I. From the foregoing, it may be seen that bysliding the key I40 along the shaft I20, as for example by means of the multiplier setting mechanism shown in said Avery application, Serial No. 367,025, one may establish a positive drive from the shaft I20 to a selected gear I2I to I29, which in turn will drive its respective gear I3I to I39 integral with shaft I30.

In Figure 1 the gear' I2I is shown and it will be noted that it has several teeth removed. The removal of these teeth serves two purposes: (1)

in case shaft I30 is driven through some other pair of gears it provides clearance in which gear I3I may turn; and (2) if this pair of gears serves as the driving means it allows for the twelve and one-half per cent idle period, termed the setting phase, during which the register gears 2' are moved into mesh with the actuator gear I89 before the drive begins.

most desirable is to maintain a constant idle period and vary the pitch. The following tabulation is one alternative where the idle period is constant and the diametral pitches vary accordingly.

TableA Selection l 2 3 4 5 6 7 8 9 .,Diametralpltcl1 26 25.5 28 25 29 27.5 37 41 30 Gears #131 #132 #133 #134 #135 #136 #137 #138 #139 Numberoiteeth 36 27 24 18 l8 15 18 18 12 Gear #121 #122 #123 #124 #125 #12 128 1 Numberofteeth I 29 efliectively 1 2 ven 8 4 24 30 30 42 Teeth of com- 48 36 plate gear 16 24 32 32 40 40 5G 64 48 Idle period- 25% 25% It will be noted in the first column of the table that gear I2I is a sixteen-tooth gear with the number of teeth it will effectively drive as twelve, which is exactly seventy-five percent of sixteen; while in Figure 1, gear I2I is shown with only ten teeth. This is because the first tooth of gear I2I would contact one tooth before the one on the center line, and upon completion of the actuation the last tooth of gear I2I would wipe its respective tooth one space past center. This would cause an effective drive of two teeth more than the actual number of driving teeth. Therefore, in this case, the number of teeth remaining is two less than the desired number of teeth to be effectively driven.

If the key I40 were inadvertently positioned between two gears so as to drive them both, it would, of course, jam the transmission with both gears considerably displaced from their neutral positions. To prevent this, means are provided whereby the key I40 can never drive two gears I2I to I29 out of their neutral positions at the same time. The disc MI (Figure 2) is provided with a recess into which is pressed the nose of pawl I43 by the tension of spring I44, which tends to maintain the pawl I43 in its extreme clockwise position shown. Underlying a shoulder I45 of the pawls I43 are a series of balls I46 (Fig. 10) which are held in a retainer I41. The length of this retainer is equal to the combined diameters of all the balls plus the thickness of one pawl I43. The halls are free to roll a limited amount sufiicient to allow one pawl at a time to enter between pair of balls. In viewing Figure 2, it will be see that when the key I40 is positioned in the order shown, for example, the gear and disc I4I may be rotated and immediately thereupon the pawl I43 is rocked counter-clockwise about shaft I49 and passes between two of the balls as shown by the dotted lines I48 (Fig. 10). If the key I40 is midway between two positions, however, an attempt will be made to drive two gears, but this will be impossible because two pawls can not enter the retainer at the same time; the result being that neither can be rocked counter-clockwise far enough to permit the disc and gear to turn appreciably until the key is correctly aligned.

With the transmission thus controlled, the gear selected may rotate but all others will be held in their neutral positions. Since the shaft I30 (Fig. 10) and all gears I3I to I39 rotate as a unit, the gear I3I is used as a convenient means to drive the actuator through the idler I50, mounted on stud I5I, and gear I52 secured to the half-turn shaft I66 of the actuator. The quarter-turn and twelfth-turn actuator shafts I61 and I68 are also shown in Figure 10, which, together with shaft I66, serve to drive the register through the actuator gearing, explained hereinbefore and in the aforementioned Avery Patent No. 2,271,240. Thus, a positive selective drive may be established between the crank and the actuator in such a way that one turn of the crank will effect from one to nine half=turns of the half-turn shaft I86 to effect the operation of the actuator through cycles of operation, depending on which gear I2I to I29 is selected to drive.

Means are provided to centralize the actuator so that gears I3I to I39 will always come to rest in a centralized position and to lock the actuator against rotation when the gears 21I (Fig. 1) are not lowered into mesh with the actuator gears I89, and further to lock the gears 21I in their lowered position while the actuator is out 3f a centralized position. On the left end of the half-turn actuator shaft 466 (Fig. 12) is secured an actuator centralizing disc I53 with two oppositely disposed recesses I54, into which are urged two rollers I55 mounted on levers 56 and 85?. These levers are pivotally mounted on stud $58 and constantly urged to= ward the disc M3 by the spring 559 tensioned between the two levers. In this manner, the pressure of the rollers I55 against the recesses will hold the actuator in a centralized posiunless positively driven.

.rne lever i5? is provided with a slightly curved surface ltd in form of an arc of a circle drawn around shaft H5 as a center, and on said shaft is secured an arm ill, on opposite sides of which are mounted two rollers H2 and I18 (Fig. 11). Of these, roller 118 is adapted to sweep across the arcuate surface I60 and prevent clockwise movement of lever I51. The parts in Figure. 12 are shown in the position they assume when the gears 21! (Fig. 11) and related parts, frequently called the lower carriage, are in a raised position. When, however, the lower carriage is dipped, as previously described, the levers H6 and Ill rock counter-clockwise with shaft II5 until the roller I18 (Figs. 11 and 12) assumes the position I18--A. In this position lever I51 is free to be forced rearwardly by disc I55 when the actuator turns.

When the lever I51 is forced rearwardly in this manner the shoulder I51A lies in the return path of roller I18 and thus locks the lever HI and the lower carriage against return movement until the actuator approaches a centralized position, when the rollers i55 again become seated in the recesses of disc I53.

Means are provided to lock the gears I89 (Fig. 11) in correct alignment after the actuating phase is completed so the carriage may be subsequently lowered into mesh with the actuator without the gears I89 and 2H clashing. The second roller I12 on lever I1I sweeps across the arcuate surface I14 of lever I15 (Fig. 11) to lock said lever against clockwise movement about stud I58 in the same manner that roller I18 locked the lever I51. A lever 586 is keyed to shaft 202 and is provided with a bifurcated lower end which embraces stud I15 of lever I15. Also, on shaft 202 are loosely keyed a series of ordinal Dawls 20I which engage between the teeth of each pivot gear I89. On viewing Figure 11, it will be seen that pawl 20I is forced against gear I89 so that when the lower carriage is dipped for actuation the teeth of gear I89 will be in a position to receive the gear 21I. When the roller I 12 is moved downwardly, lever I15 is free to be rocked clockwise by spring I11 to rock lever 588 and shaft 202 counter-clockwise, so that if a, selection is made in the order shown in Figure 11 the gear I88 may turn on shaft I10 and force the pawl 20I clear of the teeth. I'he way in which ear 208 serves to hold the pawls "I in all unset orders, so the unactuated gears I88 can not float out of alignment, was explained briefly hereinbefore and may be found in more detail in the aforesaid Avery Patent No. 2,271,240.

From the foregoing description then, it may be seen that by making a nine selection on the selective transmission, shown in Figure 10, and by depressing a nine key I5 (Fig. 1), a single turn of the hand-crank rotates the numeral wheel aligned with the key depressed eight and one-tenth revolutions. During this plural cycle operation of the actuator the cam I08 makes only one revolution and, therefore, holds the carriage gears 21I in mesh with the actuator gears I89 during the entire operation. Similarly, the cam 60 makes only one revolution irrespective of the values selected and holds the numeral wheel aligning cam followers 315 away from the cams 28! so that they may make any number of revolutions in a counter-clockwise or plus direction without subjecting the cam and related mechanism to the strain resulting from the cam rocking the cam follower over the steep rise thereof. Likewise, the bail I85 (Figs. 3, 4, 5) looks the selection plates 472, 418, 484, etc-., the pawl 20I (Fig. 11) unlocks the actuator gears, and the arm i1I (Fig. 12) unlocks the actuator centralizer disc I53 for this plural cycle operation irrespective of the number selected.

I claim:

1. In a calculating machine having in combination with a register, a cyclically operable actuator therefor, means for normally locking said actuator in centralized position, a cyclically operable driving member, and a drive train between said driving member and said actuator, a selective ratio transmission in said train for driving said actuator a plurality of cycles in response to a single cycle of operation of said driving member, a cam operable through a single cycle in response to a single cycle of operation of said driving member, and control means operable b said cam in response to a single cycle of operation thereof to render said actuator locking means ineffective throughout said plurality of cycles of said actuator.

2. In a calculating machine having a register, an actuator therefor, selection mechanism settable in accordance with selected numeral values for controlling said actuator, a cyclically operable driving member, and a drive train between said driving member and said actuator, is selective ratio transmission in said train for driving said actuator a plurality of cycles in response to a single cycle of operation of said driving member, a cam operable through a single cycle in response to a single cycle of operation of said driving member, and means operable by said cam in response to a single cycle of operation thereof in one direction to lock said selection mechanism in set position throughout said plurality of cycles of said actuator.

3. In a calculating machine. a register, a. cyclically operable actuator therefor, a cyclicall operable driving member, a drive train between said driving member and said actuator including a selective ratio transmission operable to drive the actuator a selected number of cycles in response to a single cycle of operation of said driving member, a cam driven by said driving member through a single cycle of operation in response to a single cycle of operation of said member, and control cam follower to cooperate with each of said cams,

a reversible cyclically operable actuator for said numeral wheels, a reversible cyclically operable driving member, a selective ratio transmission deriving power from said driving member during one cycle' of operation thereof for driving said actuator through a plurality of cycles in either direction, a control element driven by said driving member through a single cycle of operation in either of two directions in response to a single cycle of operation of the driving member in either respective direction, and control means operable by said control element in response to a single cycle of operation thereof in one of said two directions to rock and hold said cam followers beyond the periphery of said cam throughout said plurality of said cycles of the actuator.

5. In a calculating machine, the combination of a register, an actuator therefor a cyclically operable driving member, a drive train between said member and said actuator including a selective ratio transmission, and means for selectively setting said transmission to enable the same to drive said actuator through a selectively variable number of cycles of operation in response to a single cycle of operation of said driving member; with means for conditioning said actuator for operation prior to the selective cyclic operation thereof and for normalizing the same at the completion of said cyclic operation, a cam driven through a single cycle in synchronism with said driving member upon operation of the latter through said single cycle, and means controlled by said-cam in response to said single cycle of operation thereof to operate said con.- ditioning means as aforesaid prior to and subsequent to operation of the actuator through said variable number of cycles.

6. In acalculating machine, the combination of, a register, a cyclically operable actuator therefor, a selective ratio transmission comprising, a cyclically operable driving unit each cycle thereof having an initial idle phase, a driving phase and a second idle phase, and a driven unit operable through a selectively variable number of cycles in response to a-sing1e cycle of opera- I tion of said driving unit; with mean for selectively setting said transmission to enable the same to drive said actuator through a selectively variable number of cycles corresponding to the number of cycles of said driven unit, a device operable to condition said actuator for operation and to restore thesame to normal condition, a cyclically operable cam having a conditioning phase and a restore phase of each cycle, said cam being effective upon operation thereof through said conditioning phase cause said device to condition said actuator uring the initial idle phase of said driving unit and efl'ective upon operation thereof through said restore phase to cause said device to restore said actuator during the second idle phase of said driving unit, a cyclically operable driving member, and means connecting said member to said driving unit of said transmissionand to said cam for driving said unit and said cam in synchronism with said member;

HOWARD M. Dus'rm. 

